Variable-speed power-transmitting mechanism.



Patented Nov. 28, 11916 C. M. INANLY.

VARIABLE SPEED POWER TRANSMITTING MECHANISM.

APPLICATION FILED JULY 19, IBM.

Patented Nov. 28, 1916.

8 SHEETSSHEET 2.

E we C. M. MANLY. VARIABLE SPEED POWER TRANSMITTING MECHANISM.

APPLICATION FILED JULY I9, IQII.

Patented Nov. 28, 1916.

8 SHEETS-SHEET 3.

M MN Ii I I. @wm II. I ////V I. I I

C. M. MANLY.

VARIABLE SPEED POWER TRANSMITTING MECHANISM.

APPLICATION FILED JULY I9. 1911.

Patented Nov. 28, 1916.

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8 SHEETS-SHEET 4. I

(I. M. MANLY.

VARIABLE SPEED POWER 'EMNsMmms MECHAWSM.

APPLICATION FILED JULY 19. ESII.

Patented Nov, 28, 1916.

8 SHEETSSHEET 5- C. M. MANLY.

VARIABLE SPEED POWER IRANSMITTING MECHANISM.

APPLICATION FILED JULY 19 lBH.

Patented Nov. 28, I916.

8 SHEETS SHEET 6.

, 0. M. MANLY.

VARIABLE SPEED POWER TRANSMITTING MECHANISM APPLICATION FILED .IULY I9. I9II. L wfifitfi Patented Nov. 2%), 13156.

8 SHEETS-SHEET T 1M! vL92 J90 146 116 116 III? 133 11 3 1 w 1% M9 11 115 1 1zz 0 c) by a 79 1 '8 M. MANLY.

VARIABLE SPEED POWER Tmwswimmc MECHANISM.

APPLICQL'HON FILED JULY i9. lBll.

Patented Nov. 28, 1916.

8 SHEETS-SHEET I3 CHARLES MATTHEWS MANLY, F FREEPOJRT, NEW YORK.

VARIABLE-SPEED POWER-TRANSMITTING MECHANISM.

' Specification of Letters Patent.

Application filed July 19, 1911. Serial No. 639,464. I

To all whom it may; concern:

lie it known that I, CHARLES M. MANLY, a citizen of the. United States, residing at Freeport, Long Island, New York, have invented certain new and useful lmprovements in Variable-Speed Power-Transmitting Mechanisms, of which the following is a specification.

My invention relates to variable speed power transmitting mechanisms in which a variable stroke pumping mechanism and a motor operated by the fluid delivered from the pump are interposed between a prime mover and a driven device, and particularly to that type of such mechanisms disclosed in my U. S. Patent No. 801,097 dated Octoher 3, 1905, and my application, Serial No. 399.989 filed October 31, 1907.

One object of my invention is to provide an improved simple and efiective means in such mechanisms for varying the stroke of the pumping device and thereby varying the velocity and torque ratio of the prime mover to the driven device. 7

A further object of my invention is to provide an improved construction and arrangement of the parts whereby the weight of, and space occupied by a transmitting mechanism capable of transmitting a give power may be materially reduced.

With these and other objects in View the invention consists in the novel features of construction, combinations, and arrange- -ments of parts illustrated in the accompanying drawings, and hereinafter described and pointed out in the appended claims.

In the said drawings,-Figure 1 'is a plan view of the entire transmission. Fig. 2 is longitudinal vertical section through the pump portion of the transmission. Fig. 3 is a similar view of the motor; Figs. 2 and 3 taken together constituting a section of the entire transmission on the line '23 of Fig. 1 with the connections between the pump and motor shown in both views. Fig. 4 is transverse vertical section on line l4 Figs. 1 and 2. Fig. 5 is a transverse vertical section on line 5-1") Figs. 1 and 2. Fig. 6 is an end elevation. partly in section, of the transmission as viewed from the left in Figs. 1 and 2. Fig. 7 is a plan view partly in section of a portion of the transmission at the left ofv Figs. 1 and 2. Fig. 8 is a diagrammatic sectional view showing the lar clamping nuts 1235.

arrangement of the valves for controlling Patented Nov. 23, 19%. v

the fluid pressure operated stroke adjusting mechanism. Figs. 9, 10, 11 and 12 are detall views of the valve block hereinafter referred to. Figs. 13, 14, 15,16 and 17 are de-' tail views of other portions of the mechanism hereinafter referred to. Fig. 18 is a longitudinal section of the adjustable crank mechanism on the same plane as Fig. 2, but showing the parts onan enlarged scale; Fig. 19 is a section on line 1919 of Fig. 18; Figs. 20 and 21 are detail views and side and end views respectively of the eccentric for adjusting the valve cranks; Fig. 22'is a detail view of another element ofthe valve crank adjusting mechanism; Fig. 23 is a perspective view of the eccentric bushing for-operating the pump pistons; and Fig.

24 is a perspective view of the elements plication above referred to the cylinders and valve chambers are cast integral with the crank casing but in the construction forming the sub ect matter of this application-I make the cylinders and their crank chambers separate from the crank casing in order that they may be made of stronger and more suitable material, preferably steel. To form a tight joint between the cylinders and crank casing, the cylinders are provided with 'flanges 1232 which are machined off flat on their lower faces and are held against machined surfaces on the casing surrounding the bores2 by clamping nuts 1233 threaded on the ends of the cylinders within the casing. The valve chambers are providedwith similar shoulders 1234, and simil have found it advantageous to use a special thread such as that shown in Fig. 16 for the above connections. This thread is but slightly narrower at the top 1236 than at the base 1237.

Instead of coming to a sharp edge as the ordinary thread of V-shaped cross section, the angle between the side of the thread and a diametric line of the nut or cylinder is less than the angle representing the coefficient of friction of the engaging surfaces. When a threaded joint having ordinary threads with sharply inclined sides is drawn tight, considerable radial thrust is produced which tends to contract the male member and expand the female member; hence when the male member is av cylinder having a closely fitting piston. working therein such contraction would cause the piston to bind. In a construction of this character the nut has to be drawn up tight enough to put a tension on the metal "of the cylinder between the flange and nut considerably greater than the tension produced by the working pressure of the fluid in order to hold the joint. fluid tight at all times and as the working pressure of the fluid frequently rises to several thousand pounds per square inch, it is readily seen that the radialthrust produced by a nut having a thread of usual construction would be very great. With my improved nut there can be no radial thrust at any pressure, for the friction increases directly as the pressure and the angle producin the radial thrust is less than the coefliclent of friction.

Each cylinder and its valve chamber are connected by an integral member 6 extending from the top of the cylinder to an intermediate point of the valve chamber and having a passage 6 therethrough for the fluid. Each cylinder, valve chamber and connection is preferably formed of a single steel forging, the cylinders and chambers beingbored through from end to end. Each cylinder is'closed at its outer end by a plug 7 and each valve chamber is closed by a cap 8. The connecting passages are formed by boring through the cylinders and connecting members into the valve chambers,

"the openings in the walls of the cylinders being closed by. suitableplugs9. Slidably mounted in each of the cylinders 3 is a piston 10 and attached to each piston by means of a cross pin 11 to have a rocking connection therewith is a piston rod- 12. The. piston rods are provided at their inner ends with curved shoes 13 which fit against the outer surfaces of a tubular bushing 14. The shoes are held against longitudinal displacement on the bushing by means of rings 15 attached to the end faces of the bushing and having flanges which project over the ends of the shoes, the construction being such that circular motion imparted to the bushing, as by a crank, will simultaneously and progressively operate all the pistons.

Rotatably mounted in the casing 1 by means of bearings 37 38 on either side of the cylinders?) is a crankshaft 17 the crank pin when the center of the eccentric bushing 18 of which is encircled by an eccentric bushing 19, spaced therefrom by a two part bushing 20 for convenience in assembling. After the parts are assembled on the crank pin, which is accomplished by inserting one half of the bushing 20 at a time, and working the halves around until they occupy the desired position, the split bushing is locked to the eccentric bushing by means of a pin 41 in the eccentric bushing, which pin is provided with a lug as shown in Figs. 18 and 19, whichengages a suitable recess formed in the meeting edges of the split bushing when the pin is turned to the position shown in the above mentioned figures of the drawing. The eccentric bushing 19 works in an antifriction bushing in the tubular bushing 14 to which the piston rods are connected as described above, and the eccentricity of, the

. bushing is exactly equal to the eccentricity from their maximum stroke, equal to twice the eccentricity of the crank, when. the center of the outer periphery of the bushing is in the same radial line with the center of the crank and on thefsame'side of the center of rotation of the crank shaft, to no-stroke, coincides with the center of rotation. In the drawings, the parts are shown in the maximum stroke position and the nostroke position is obtained by rotating the eccentric bushing arpund the crank through an angular distance of 180 degrees. Rotation of the eccentric bushing beyond this point causes the stroke of thepistons to increase, and, by means of the valve mechanism which will now be described, causes the direction of the flowof the fluid to be reversed, thereby reversing the motor element of the transmission.

Formed in each of the valve chambers are three recesses or ports, 21, 22, 23, the middle one 21 connecting with the passage 6' leading from its respective pump cylinder 3. The inner 22 and outer port 23 connect with bores 24, 25 respectively in the side wall of the valve chamber opposite the passage 6, which bores connect the ports 22, 23 with inner and outer manifolds 76, 77, forming an intermediate connection between the pump and motor, as will be later described. Slidingly mounted in each of the valve chambers 5 is a piston valve 26 having three heads 27, 28, 29 separated from each other by two intermediate necks 30 and 31 the neck 30 being the outer neck between the outer head 27.and the middle head 28, the neck 31 being between the middle head and the inner head 29.

The middle head 28 of the valve is of a neonate width substantially equal to the width ofthe port 21 so that reciprocation of the valve connects the ports 24, 25 alternately with the passage 6, with momentary periods when each of the ports 1s closed at the time when the mlddle head exactly covers the port 21.

The valves are all operated from a com-- mon crank pin 32 to which they are operatively connected by means of connecting rods the bearing 37 being attached to the sleeve.-

As the direction of the flow of fluid in the passages 6 is reversed when the direction of movement of the pump pistons is reversed at each end of their strokes, it is ,obvious that the crank arm of the valve crank pin must be positioned an angular distance of 90 degrees from the real crank arm of the pump pistons.

The real crank arm of the pistons is a line drawn from the center of the .outer pe riphery of the eccentric bushing 19 to the center of rotation of the crankshaft 17 and this line changes angularly with the adjustment of the eccentric bushing, but at only half the rate that the bushing is rotated on the crank pin; therefore the valve crank pin must be connected to the bushing by some mechanism that causes the crank pin to move around the center of rotation of the crank shaft 17 out of line with the bushing 19 and with a two to one reduction of the angular rate of the adjustment of the bushing. disclosed in my application above referred to in connection with a different type of valve. Tt consists'of a double eccentric piece 40 fitted into the right-hand end of from turning with respect thereto by the pin 41 previouslydescribed and the additional pins 41*. The double eccentric (see Figs. 20 and 21) comprises one eccentric 42 concentric with the outer periphery of the bushing 19 and another eccentric 43 concentric with the crank shaft 17 when the parts are in the maximum stroke position as shown in the drawings, the two eccentrics being therefore eccentricto each other an amount double the eccentricity of the crank pin 18. Rotatably mounted on the eccentric 42 is a square shoe 44 which fits in and is free to slide in a vertical slot 45 in a plate 45 shown detached in Figs. 22 and 24. The plate 45 comprises adisk having slots in its opposite faces, the slot 45 containing the shoe 44 on the face of the plate adjacent being at right angles to the slot 45?. The

This mechanism has been fully the eccentric bushing 19 and prevented the crankshaft, and the opposite slot 45" slots are equal in depth to half the thickness of the plate, whereby the two slots form a square central opening where the slots cross each other. The plate is fixedly attached to a flange 46 onthe end of the sleeve 36 of the valve crank pin, and rotat'ably mounted on the eccentric 43 is a square shoe 47 which fits in, and is freeto slide in the slot 45 which is in line with the crank arm of the valve crank pin 32. In the operation of adjusting the stroke the eccentrics 42 and 43 turn on the crank pin 18 as a center with the eccentric bushing 19, and by means of the crossed shoes turn the sleeve 36 on the crank shaft 17 as acenter at exactly one half the angular rate that the bushing is turned on the crank pin 18. When the pump stroke is adjusted from one side to the other of its no-stroke position, the relative positions of the real crank arm of the pump pistons and the crank pin of the pump valves is reversed, that is, the valve crank pin instead of being 90 degrees .angularly in advance of the real crank of the pump piston in the direction of rotation of the pump shaft 17 becomes 90 degrees angularly behind the real crank arm of the pump pistons, and thereby the direction of flow of the fluid and the direction of rotation of the motor is reversed.

The sleeve 36 of the valve crank pin is held against longitudinal displacement on the shaft 17 by means of a tubular bolt 203 screwed into the crank shaft at a point co-incident with its center of rotation and extending through a longitudinal bore in the valve crank pin 32. The bolt 203 has a head 204 which engages the end face of the crank pin and an integral extension 205 beyond the head. The bolt is tubular as described and its bore connects with a bore 206 in the crank shaft 17 leading to the center of the crank 'pin 18 as shown in Fig. 2. Radial holes 207 in the crank pin 18 communicate with the bore 206 and registering with the holes 207 are oil grooves 208 in the inner face of the two part bushing 20.' Radial holes 209 are formed in the bushing 20 and the eccentric bushing 19 to permit oil to pass to and lubricate the bearing between-the eccentric bushing and the bushing within the bushing 14, which carries the pump pistons. The extension 205 of the bolt 203 rotates in a bearing 210 formed in a member 211 projecting into the central chamber of the manifold casting 212 and integral therewith. A radial bore 213 in the member 211 connects with the bearing 210 and connecting with the bore 213 is a pipe 214 through which oil is de- .the same size as the pump casing 1 and the 76 and 77 respectively, and formed inte-' gral therewith, are five longitudinally extending tubular members 217, the bores of which register with the inner ports 24 of the pump valve chambers, and five similar mem- A bers 218 whose bores register with the outer ports 25. The central chamber of the manifold is connected to the pump casing by bolts 225 as shown in Fig. 1, and each of the members 217, 218 is connected to its valve chamber around the ports 24, 25 by a fluid tight connection of special construc- Yso tion. which will now be described. The valvechambers a're all formed with flanges 219, 220 surrounding the ports 24, 25 respectively and theseflanges are machined so that their faces around the ports all lie in the same transverse plane. Similarly, the tubular members 217, 218 are provided with flanges 223, 224 having machined faces also all lying in the same transverse plane. The ports 24 and 25 and the bores of the members 217, 218 are formed with tapering counterbores 227, 228 respectively, and fitting in the counterbores are non-resilient bushings 229, preferably of annealed copper, whose outer surfaces'taper in opposite directions from the center to coact with the surfaces of the counterbores. The copper bushings are made somewhat larger than the counterbores and their bores are correspondingly larger than the ports 24, 25 and the bores of the members 217, 218 so that when in assembling the machine, the faces of the flanges 223, 224 are drawn up against the faces of the flanges 219, 220 by the bolts 230 in the flanges, the bushings will be contracted and reduced in size until their bores are the same size as the ports 24, 25 and the bores of the members 217, 218. I have found that a joint of this character will be tight under any pressure up to the breaking point of the casting, in fact, the higher the pressure the tighter the joint becomes, for the copper bushings are expanded by the fluid pressure in their bores against their counte-rbores with av pressure increasing as the pressure of the fluid. Joints of this improved type are particularly advantageous in a machine of this character where there are a plurality of jOints to be made between the same two inflexible members for the reason that the degree of pressure that they will withstand is not dependent upon the pressure with which the engaging faces. of the members are held in contact, as is the case with an orv dinary ground or gasket connection. It is practically impossible at a cost thatis not prohibitive to make all the meeting faces of the flanges 219, 220, 223, 224 absolutely accurate so that they can all be drawn up with sutlicient pressure to hold a ground or gasket connection fluid tight against the working pressure of the fluid, but with my improved connection the bolts 230 have only to be drawn tight enough to compress the copper bushings and bring the engaging faces into contact to make a perfectly tight joint at any pressure.

The motor element of the transmission (see Fig. 3) comprises a crank casing 231 having five radial bores 232 to receive the motor cylinders 233,- and five bores 234 to receive the motor valve chambers 235. The motor valve chambers are identical with the pump valve chambers, the three ports 236, 237, 238 thereof, connecting respectively with the inner manifold 76, the passage 239 to the motor cylinders, and the outer manifold 77. The motor valve chambers are connected to the manifolds by joints similar to those between the pump valve chambers and the manifolds, and the crank casing 231 is attached to the central chamber 215 of the manifold casting by bolts 240. Each motor cylinder 233 and its valve chamber 235 are preferably formed of one integral steel forging with a connecting member 241 generally similar to the pump cylinders and valve chambers except that the connecting members are curved outwardly from the valve chambers to the motor cylinders in order that the motor pistons 242 may have a longer stroke than the maximum stroke of the pump pistons. To make the motor cylinders and valve chambers I first forge the parts with the connecting member straight as shown in full lines, in Fig. 15 and then bore through the cylinder and chamber, from end to end for the piston and valve and bore through the wall of the cylinder and the connecting member 241 to form the passage 239. I then heat the connecting members and bend them to bring the valve chambers and cylinders to the desired relative positions.

The outer ends of the valve chambers are closed by caps 243 and the outer ends of the cylinders are closed by plugs 244 and the holes through the walls'of the cylinders by plugs 245. The motor cylinders and valve chambers are attached to the crank casing in the same manner as the pump cylinders and valve chambers.

Rotatably supported in the crank casing 231 by bearings 246, 247, on either side of its .crank pin 248, is a crank shaft 249 which constitutes the driven shaft of the transmission. The pistons 242 are slidably mounted in the motor cylinders 233 and connected to the pistons by cross pins 251 are piston rods 252 generally similar to, but larger than, the piston rods of the pump to accommodate the greater throw of the crank. The inner ends of the piston rods the bushing 254 is spaced from the crank 248 by a two part bushing 256.

mounted in the valve chambers 235 are.

Slidingly piston valves 257 identical with the valves 26 of the pump whereby fluid connection is established between the manifold 76 and the passage 239 and'between the manifold 77 and the passage 239, alternately, whereby "fluid under pressure from the pump delivered through either manifold will reciprocate the pistons 242 and rotate the crank shaft in one or the other direction according to which manifold is the source of the fluid pressure. The valves 257 are connected for operation to a crank pin 258 projecting from the inner end face of the crank shaft 249, by rods 259 having shoes 260 held by flanged rings 261 all identical with the corresponding parts of the pump valve connections. The valve crank pinis 90 degrees distant angularly from the crank pin 248.

I have above stated that the middle heads of the pump valves are made of a width substantially equal to the width of the middle ports of their valve chambers and that the. valves and valve chambers of the motor are identical with those of the pump. Tn the drawings T have shown the middle heads of the valves as having V notches 262 and 263v formed in its edges for the purpose of giving a gradual opening and closing of the middle port. The exact construction of this feature of the'valves and the advantages resultant therefrom are fully disclosed in my pending application No.

- 606.618 filed February 4, 1911. and such feature is covered in the claims thereof, to which application reference is therefore here made.

The transmission may be conveniently supported by brackets, shown in Figs. 1, 2, 3 and 4, having projecting arms 301 for attachment to a suitable base and central annular bearing portions 302 which engage the ends of the central chamber of the manifold casting and are held in place by the bolts 225 between the pump crank casing and the manifold casting, and the bolts 240 between the motor crank casing and the manifold casting.

The mechanism for controlling and varying the position of the eccentric bushing 19 on the crank pin 18 of the pump crank shaft The gear 53 is concentric with the shaft 17 and the sleeve 54 extends through and beyond-the bearing 38 and carries the rotary member of the said bearing; To the left of the bearing 38 the crank shaft 17 is formed with a screw thread 56 on which a nut 57 is mounted. The sleeve 54 surrounds the nut 57 and is provided with four longitudinal slots 58, of a length substantially equal to the threaded portion of the shaft, in each of which is arranged a shoe 59 and surrounding the slotted sleeve 54 and the shoes 59 is a sleeve 60 provided with a collar 61, the nut 57, shoes 59, and sleeve 60 being fastened together by pins 62 in the collar 61. Surrounding the sleeve 60 is a two part yoke 63 and interposed between the flanges of the yoke and the collar 61 are ball bearings 64, the construction being such that longitudinal movement of the yoke will move the nut along the threads 56 and cause relative rotary movement of the sleeve 54 and the shaft 17 and thereby through the medium of the gears 53 and 52 turn the eccentric bushing 19 around the crank pin .18 to vary the stroke of the pump pistons as described above.

Means are provided to utilize the fluid pressure in the transmission for shifting the yoke. This means comprises fiye cylinders 65 formed in the pump casing 1 between the bores 2 for the cylinders 3, in each of which a piston 66 is mounted for reciprocation. The cylinders 65 are closed by plugs 67 having central packed bores through which the rods 68 of the pistons 66 reciprocate, the said rods being connected to radially extending cars 69 on the yoke 63. All of the cylinders 65 are connected together at each end by bores 86, 88 (see Fig. 7) so that fluid under pressure may be admitted simultaneously to all the cylinders on either side of the pistons to shift the yoke 63 in either direction as desired. Inclosing the yoke and piston rods and the left hand end of the shaft 17 is a casing 70 hereinafter termed the control casing. This casing is provided with an annular flange 71 which is bolted to a similar flange 72 on the pump casing 1, and at its other end is provided with a bearing 73 for the shaft 17 and a stuffing box 74 surrounding the shaft. Between the bearing 73 and the stufling box 74 a double thrust bearing 75 is arranged to hold the shaft against longitudinal displacement in the casing. The top wall of the control casing 70 is formed to provide a semi-cylindrical seat 78 in which is mounted a cylindrical valve block 79, held in place by a semi-cylindrical cap 80 bolted to the casing on each side of the valve block. The contacting surfaces of the valve block and the casing and cap are packed by an intermediate perforated sheet of fibrous material to be fluid tight so that fluid admitted to ports in the casing and cap may pass into registering ports in the intothe bottom of the seat 78 at diflerent points longitudinally thereof. The bore 81 is connected by a fluid tight connection of thespecial character described above to a bore 85 leading into one of the bores 86 which connect the front ends of the adjusting cylinders 65, and the bore 82 is connected by a similar connection to a drill hole 87 extending a short distance longitudinally into the pump casing 1. Extending outwardly from the drill hole 87 is a drill hole 89 which communicates with a passage 90 formed in a ridge 91 on the outer. wall of one of the adjusting cylinders and extending to a port 92 leading into the cylinder at a point adjacent its rear end. As the cylinders 65 are all connected, it will be clear that fluid connection is established through the ports and passages described between the ports 83, 84, in the valve block casing, and the front and rear ends respectively of the adjusting cylinders 65.

The mechanism for controlling the passage of fluid to and from the adjusting cylinders will now be described.

Extending longitudinally through the valve block 79 is a bore 93 in which is mounted a piston valve 94, as shown in Figs. 2, 3, 7 and 8. In Fig. 8 to which attention is now especially directed, I have shown the valve block diagrammatically insection with all the valves in the same vertical plane for the sake of clearness of illustration, and in order that the circulation of the fluid during the adjusting operation may be easily followed; but it will be understood that as actually constructed the valves are arranged in different planes both axially and radially from that shown in this figure, Figs. 9, 10, 11 and 12 showing the true arrangement of the passages in the valve block. The valve 94 is provided with five heads, 95, 96, 97, 98 and 99 and with four reduced portions or necks 100, 101, 102 and 103 between the heads. Extending radially into the 'bore 93 of the adjusting valve from the lower side of the valve block are seven equally spacedslots' which are connected by means of pipes 113, r

shoulder formed by the reduction is ground to form a seat for a check valve 118, the stem 118 of which crosses the bore 116 and is guided in a small hole 119 forming a re duced continuation of the passage 117. Threaded in the passage 117 and closing the same, is a plug 120 having a central longitudinal bore 121 in its inner end. The end of the plug is ground to form a valve seat around the bore 121 against which a check valve 122 is held by a spring 123 arranged between this valve and the valve .118 to normally hold both valves closed. The valve 122 has a ribbed or cut-away stem 124 working in the bore of the plug, which stem has a reduced cylindrical stem 125 working in a small hole forming a reduced continuation of the bore 121, for a purpose to be hereinafter described. A hole 126 register-f ing with the bore 115 extends across the plug 120 to permit fluid to pass from the bore 115 to the bore 121 of the plug, and also to pass through the plug from the inner end of the bore 115. Leading from the passage 117 at a. point between the valves 118 and 122 is a horizontal transverse passage 127, shown best in Fig. 11, communicating with a vertical transverse passage 128 which latter passage connects at its lower end with a bore 129 parallel with the bore of the adjusting valve 94 and extending into the valve block from its front end. Connecting the bore 129 at a point to the left of the pas sage 128 with the bore 93 of the adjusting valve is a counterbored port 130 registering with the port 106 between the ports 105, 107 leading to the ends of the adjusting cylinders as described above. A valve 131 having a head 132 arranged to normally lie between the passage 128 and port 130 is slidably mounted in the bore 129. The valve 131 is formed with a reduced stem 133 extending between the head 132 and a second head 134, the purpose of which will be hereinafter explained. The bore 129 is enlarged beyond the head 134 and arranged therein and engaging the head 134 is a spring 137 surrounding a reduced stem 138 of the valve and abutting a ainst the end plate 193 of the valve block; onnecting with the slot 104 at' the light of the head 96 of the valve 94 is a "ertical passage 139 which communicates with a horizontal passage 140 bored into the memes block from the'front face. A horizontal passage 141 is bored into the valve block above passage 140 and this passage connects with bore 116 from the manifold 77 of the fluid circuit. Mounted in the passa e141 is a plug 142 having. a longitudinal ore 143 in which is mounted a check valve 144 held against the end of the plug by a spring 145. The plug 142 has a hole. 146 leading into its bore 143 and registering with this hole is a passage 246, shown in dotted lines in Fig. 8,

leading to the passage 140 and thence to the slot 108 to the left of the head 97 of the adjusting valve. A hole 147 is bored into the valve block from its rear face intersecting the bore 115 and in this hole a check valve 148 is mounted. The valve works against a seat ground on a shoulder between the hole and a reduced extension 149 of the hole. port 450 connects the passage 140 with port 149 of the hole 147 and a plug 451 issscrewed" into the hole 147 to close the same and form an abutment for the spring 152 of the valve 148.-

As described above, the direction'of the flow of the fluid is reversed when the pump actuating eccentric is adjusted from one side to the other of its n'o-stroke or zero position and consequently one of the manifolds 76, 77, contains fluid under high pressure when the eccentric is on one side of zero and the other manifold contains thesuming that the manifold 76 is in the highpressure side of the circuit, the fluid passes into the valve block through the port 115, thence through the valve 122 in the plug 121 to the passage 128 behind the head 132 of the valve 131. The spring 137 of this valve is of proper size to yield under the pressure of the fluid from the high pressure side of the circuit and allows the valve to move to the left and thereby uncover the port 130 leading to the port 106 of the bore of the adjusting valve, allowing the fluid to enter that port. The port 106 is between the ports and 107 which lead respectively to the rear and front ends of the adjusting cylinders so that movement of the adjusting valve in either direction from the position shown will admit the fluid pressure to the front or rear ends of the adjusting cylinders, thereby shifting the adjusting pistons to the left or right. The movement of the adjusting pistons by the fluid admitted at one end of the cylinders 65 forces a corresponding amount of fluid out at the other end. Assuming the valve 94 to have been'moved to the left from i the position shown in Fig. 8, therebyconmeeting the port 106 with the port 107 and the port 104 with the port 105, the fluid under pressure passes into the port 106 through the bore 93 to port 107 and thence through the port 83 to the passages leading to the bores in the forward ends of the adusting cylinders 65, and shifts the P18110118 66 and the adjusting yoke and connected the port 105the fluid passes through the Q bore 93'of the adjusting valve between the heads 95 and 96 to the passage 139 and thence through the passage 140 and the hole 146 into the bore of the plug 142 and through the check valve 144into the passage 116 connected to the then low pressure side of the fluid circuit. When the fluid is circulating in a reverse direction the passage 116 is connected to the high pressure side of the fluid circuit and the passage to the low pressure side.

the adjusting valvefrom the passage 116 through the check valve 118 and the fluid from the adjusting cylinders will be returned to the low pressure side of the circuit from the passage through the check valve 148 and the passage 115.

The adjusting valve 93 projects rearwardly beyond the valve block (see Fig. 7)

and connected to its projecting end is a rod 150 which rod is slid'ably mounted in a guide cylinder 151 formed in the pump casing. The rod 150 is connected'to the valve 93 by means of a T-slot 152 on the rod which embraces a head formed on the valve 93 by a groove 153 so that any lateral displacement of the rod 150 will not be communicated to the valve but will be taken up by the connection. Connected to the rod 150 by means of a pin 154 is a floating lever 155 one end of which is connectedby means of a link- 158 and eye-bolt 157 with a projection 156 on the yoke 63. The other'end of the floating lever 155 is connected by a link 159 to a coupling 310, to which is connected a rod 160 slidingly mounted in the control casing and projecting through the front wall thereof as shown in Fig. 7. A control lever 161 is fulcrumed on the control casing at 162, Fig. 6, and is connected at one end to the pro jecting end of the rod 160 by means of a link 163. The other end of the control lever extends beyond its fulcrum as shown and is provided with an eye by which it may be The high press ,sure fluid will then enter the passage 128 to I Q and the valve 94 moves to the right until it 'motor is determined by the connected to any desired operating mechanism or the end of the lever itself may be formed as a handle to be operated directly. .A rod 311 is attached to the coupling 310 to form an extension of the rod 160 and this rod works in a housing 314'. Mounted in the housing 314 is a plug 313 having a bore in which is mounted a stop member 316 held against the rod 311 by .a spring 315 and adapted to engage a notch '312 in the rod 311 when the pump stroke is set at its zero position. Suppose the free end of the lever 161 be moved a short distance to the right asshown in Fig. 7. This operation moves the rod 160 and the attached end of the floating lever 155 to the'left and asthe lever is connected to both the valve and the yoke and the valve oflers substantially no resistance to longitudinal movement, the floating lever turns on its connection to the yoke as a fulcrum and moves the valve to the left from the position shown in Fig. 8, there by connecting the high pressure port 106 wlth the port 107 leading to the forward ends of the adjusting cylinders 65 and connecting the rear ends of the cylinders with the low pressure port '104. The fluid pressure in the adjusting cylinders moves the yoke 63 and its connected parts to the right as shown in Fig. 2 and thereby reduces the stroke of the pump in the manner already described. When the yoke 63 moves to the right, the end of the floating lever attached thereto also moves to the right, and as the rod 160 and connected parts ofler greater resistance to movement than the valve 94, particularly when the lever 161. is held by the operator, the end of the floating lever attached to the rod 160 acts as a fulcrum is restored to normal position in which the I adjusting cylinders are cut oif from connection with the fluid circuit andthe yoke held against further movement.

It will be clear from the above description that the adjusting yoke 63 is moved by the fluid pressure to exactly the same extent that the rod 160 is moved by the handlever 161 and therefore the stroke of the pump pistons and consequently the speed of the position of the lever 161.

As explained in my patent and applica tion referred to, it is essential to the proper operation of a hydraulic gear to maintain the fluid circuit completely full of fluid and means are therefore provided to collect all the fluid that may leak past the pump and motor pistons and valves, adjusting pistons, etc., and to pump it back into the fluid circuit. In the cases referred to and also in the present case, the fluid employed is preferably oil which serves the double function of transmitting the power and lubricating the working parts, and in order to have a motor casing and the above mentioned leakage is collected by the walls of the casing and drains into the bottom of the control casing where it mingles with the surplus oil.

-Mounted in the control casing below the shaft 17 is a car pump hereinafter referred to as the lea rage pump. This pump comprises a casting 164, attached to the casing 70 by bolts 165 passing through bosses 166 formed in the casing, in which casting is mounted a pair of intermeshing pinions 167, 168 attached respectively to rotating shafts 169, 170 supported at one end in the side wall of the casting 164 and at the other end in a cover plate 171 which forms the opposite wall of the leakage pump casing. Mounted on the shafts 169, 17 0 between the gears 167, 168 and the cover plate 171, are washers 171 and 171 respectively, which washers exactly fill the space between the gears and the cover plate, and are maintained in fluid tight relation with the side faces of the gears. The purpose of this construction is to provide means whereby the wear on the side faces of the gears may be readily. taken up. As the gears wear, sheets of paper or other packing may be placedbetween the cover plate and the washers to hold the washers in close contact with the gears. Formed integral with the shaft 169, or attached thereto, at its end adjacent the front 'wall of the casing 70 is a pinion 172 meshing with a pinion 473 having driving connection with the shaft 17. The lower portion of the casing 70 is formed as a detachable pan 173. Leading into the suction side of the leakage pump casting 164 is a horizontal bore 174 (Fig. 6) with which a bore 175 connects, and connected to the bore 175 is a pipe 176 closed at its lower end, which extends into the pan 173, the lower portion of the said pipe being perforated and surrounded by a strainer 177 to clean the oil of any grit or other solid particles which it may contain.

The leakage pump is designed to deliver to the main circuits more oil than is necessary to replace the leakage from these circuits and the surplus oil is returned to the suction side of the leakage pump circuit through valves and connections arranged in the valve block in the manner and for a purpose hereinafter set forth. Formed in the casting of the leakage pump on the pressure side is a bore 178 to which is connected a pipe 179 leading through the casing 70 to the cap'80 of the valve block where it conmeans Connected to the suction side of-the leak age pump through the bore 174: is a pipe 183 (Fig. (3) which extends thereto through the side of the casing from the side wall of the seat 78 in which the valve block is.

mounted and where it connects with a bore 184 through the wall of the seat which registers with a transverse bore 185 leading from a longitudinal bore 186 forming an enlarged extension of the constant low pres sure passage 140. The excess fiuidfrom the pressure side of the leakage pump passes through passages which will be later described, the valve mechanism above referred to and thence through the pipe 183 to the suction side of the leakage pump, and such fluid in passing the point where the bore 175 enters the bore 174 has an injector eflect tending to draw other fluid up from the pan 173 to the suction side of the leakage pump thereby reducing the force necessary to drive the leakage pump. As previously stated it is advantageous to make the capacity of the leakage pump great enough to always give an over supp y and consequently fluid is returning to the leakage pump through the pipe 183 practically all the time while the machine is running. On

this account it is advantageous as regards the efliciency of the machine to arrange the discharge in this manner. to reduce the power necessary to run the leakage pump. Also having the discharge connected to the suction side of the leakage pump instead of permitting it to flow 0d into the casing 70 as heretofore, prevents the said discharge from becoming mixed with air and drawn back later into the fluid circuitin such condition. the operation of the machine being much better when the oil is free of air.

1 have explained how the port 106 is automatically supplied with high pressure fluid from the main circuit when there is high pressure fluid. in either side of said circuit and how such high pressure fluid is used for operating the pump stroke adjusting mechanism. It is readily seen however that when the pump is at its no-stroke or zero position there is no pumping action and consequently there is no high pressure in either side of the circuit. 1 have therefore provided the valve mechanism heretofore referred to and which'will now be described, for enabling the leakage pump to supply fluid under sufliciently high pressure to operate the stroke adjusting mechanism when there is no high pressure in the main circuit. Connecting with the longitudinal passage 182 of the valve block (Fig. 8) into which the fluid is deliveredfrom the leakage pump through the port 181, is a transverse bore 188, shown dotted in Fig. 8 which leads'to the port 110 of the adjusting valve bore, and leading from the adjacent port 109 of the adjusting valve bore isa transverse passage 187, also shown dotted. in Fig. 8, which connects .with the longitudinal passage 140. The heads 98 and 99 of the adjusting valve 94 and the stem 103 between them are so proportioned that when the valve 94 is in its normal position shown in Fig.8 fluid'may pass from port heads 99 or 98 respectively close the bore of the adjusting valve between the ports and thereby cut ofl communication between passages 187 and 188. Mounted in the enlarged extension 186 of the passage 140 is a valve 189 hereinafter referred to as the low pressure relief valve. This valve comprises'a head 190 slidably mounted in and normally closing the end of the passage 140 where it joins the enlarged bore 186, the said head having a three-pointed guiding stem extending into the passage 140 and a reduced stem 191 extending into the bore 186. The stem 191 is provided with a collar 192 intermediate its ends and surround ing the stem and engaging the collar and the end plate 193 is a spring 194 adapted to normally move the valve to the right as shown in Fig. 8. Also surrounding the stem 191 and arranged between the head and the shoulder forming the end of the bore 186 around the passage 140 is a spring 195' similar to the spring 1914, the springs 194 and 195 being of such length that the entire head 190 lies just within the passage 140. In the normal operation of the machine when the adjusting valve 94: is in the position shown in the drawings, the fluid from the leakage pump passes through the port 103 to the constant low pressure passage 140 whence so niu ch as is necessary to fill the main circuit passes through whichever low pressure check valve 144 or 148 leads to the 'then low pressure side of the circuit, and the balance blows ofi' through the low pressure relief valve 189 and returns to the leakage pump as described.

When there is no high pressure fluid in the .main circuit and it is desired to utilize the pressure from the leakage pump to operate the pump stroke adjusting mechanism, the adjusting valve 94 is shifted to eitherthe right or left, according to the direction of rotation of the driven shaft desired, a sufficient distance for the head 99 or the'head 98 to close the passage between the ports 110 and 109. As the leakage pump is constantly driven directly from the driving shaft, the pressure of the fluid inthe passage 182 begins to rise as soon as the valve 94 is operated as described. Connecting the passage 182 and the passage 129 at a point between the heads 132 and 134 of the valve 131 is a transverse bore 196 and intersecting the bore 196 and also the passage 246 leading to the constant low pressure passage 140, is a longitudinal passage 197 bored into the valve block from the front.

A check valve 198 hereinafter referred to as the high pressure relief valve, is mounted To overcome this di in the passage 197 opening from the bore 196 to the passage 246 and normally held 1n closed position by a spring 199 surrounding the stem 200 of the valve and abutting against a plug 201 held in the passage by the end plate 193. It will be remembered that the spring 137 of the valve 131 holds the valve when there is no pressure against the head 132 in position to permit communication between passage 129 at the left of the head 132 and the port 130 through which the high pressure fluid is delivered to the adjusting cylinders, hence the fluid from the leakage pump is free to pass into the port 130. When the adjusting valve 94 is shifted to close the port between the passages 187 and 188 of the normal leakage pump circuit the heads 96 and 97 uncover the ports leading to the ends of the ad usting cylinders, connecting one of said ports with the port 130 and the other one with one of the constant low pressure passages 139 or 246. The pressure of the fluid from the leakage pump continues to rise in the bore 196 until it is suflicient to open the high pressure relief valve 198 and permit the fluid to blow off into the low pressure passage 246, but the spring 199 of this valve is of such tension that before this point is reached the pressure is sufficient to operate the pump stroke adjusting mechanism. As soon as the pump is adjusted out of its zero position the pressure in one side or the other of the main circuit rises, which pressure .is transmitted to the fluid in the passage 128 where it may be called on for further adjustment of the stroke changing mechanism.

The spring 137 of the valve 131 is sufiiciently stifl to hold the valve in the position shown except when the pressure on the head 132 from the high pressure passage, is sufliciently high to operate the stroke adjusting mechanism, but it sometimes happens that the pressure of the fluid about balances the spring 137 so that the head 132 may be moved sufliciently to the left to prevent the fluid from the leakage pump entering the port 130 but not far enough to permit the fluid from the passagie 128 to enter the port.

culty I have provided the valve with a bore 202 through which fluid from the leakage pump may pass into the chamber inclosing the valve stem and exert its pressure on the end of the stem to force the valve to the right and establish communication between the middle portion of the bore 129 and the port 130. It will be noted that the bore 129 is counterbored at the point where it crosses the passage 246 so that the head 134 of the valve 131 will not obstruct the passage of fluid through the passage 246.

As shown in Fig. 11, the pipe 214 which conveys oil to the pump crank bearing connects with the passage 450 leading to the constant low pressure passage 140 through a ort 460 in the cap 80 of the valve block.

11 order to prevent the fluid pressure in the main circuit of the transmission rising above a safe working limit and also to permit thetransmission to be rendered inoperative without adjusting the pump pistons to their no-stroke position, I have provided a valve mechanism, which will now be described, between the manifolds 76 and 77 whereby the pump and motor will be automatically short circuited whenever the pressure rlses above a predetermined point or may be short circulted at will by the operator. This valve mechanism is located as shown in Fig. 1, and is shown in detail in Fig. 13. At the point where the valve mechanism is mounted the manifolds 76 and 77 are connected bya member 265 forming an integral part of the manifold casting. A bore 266 extends longitudinally through the member 265 and the manifolds 76, 77 are connected to the bore 266 at different points longitudinally thereof by ports 267, 268 respectively. Slidably mounted in the bore 266 is a tubular valve member 269, hereinafter referred to as the by-pass valve, which valve member is provided with three heads 270, 271, 272, the middle one 271 fitting the bore 266 between the ports 267 and 268. Between the heads, the external diameter of the valve member is reduced so that when the member is shifted a suflicient distance to the left from the position shown in Fig. 13 the ports 267 and 268 will be connected and the fluid permitted to pass from one manifold to the other whereby the pump can operate at any stroke without delivering fluid to, or operating the motor, and the motor can be turned by hand or other means and the fluid thus circulated by the motor will be unobstructed. The bore of the valve member 269 comprises three different portions, 273, 274, 275, of different diameters the part 273 at the left as seen in Fig. 13 being larger than the middle portion 274 while the portion 275 at the right is smaller than the portion 274. The three portions of the bore above described are separated from each other by chambers 276 and 277, which chambers are connected by radial holes 278, 279 with the ports 267, 268 leading to the manifolds 76, 77 respectively. Slidably mounted in the bore of the valve 269 is a piston valve 280, having three heads 281, 282 and 283 fitting in the three portions 273, 274, 275 respectively of the bore of the ing to the right of the member 265 and inclosed in a housing 287 attached to the 'said member. A spring 288 surrounds the stem 286, its ends abutting respectively against a nut 289 on the end of the stem and a washer 290 engaging the end of bypass valve 269. The bore of washer 290 is smaller than the bore of the valve 269 at that point so that the shoulder 291 betweenthe valve 280 and its stem 286 will engage the washer 290 to limit the relative movement of the valves 269 and 280 underthe action of the spring 288. The end of the valve 269 projects beyond the member 265 to the manifold 77.

at the left and to its projecting end a yoke 292 is attached by means of a cross pin 293. Integral with this yoke is a stem 294 extending through a stuffing box 295 formed in a housing 296 attached to the member 265. Links 297 are attached to the end of the stem 294 to which any desired operating member for the by-pass may be attached. The valve 280 is provided with a small bore 298 leading from the left end thereof to the stem 286 and through the side of the stern so that any fluid that may leak past either of the valve heads into the housing 296 may pass into the housing 287 and thence through the pipe 299 to the casing.

' Assuming the manifold 76 to be the high pressure side of the fluid circuit the fluid therefrom will pass into the port 267 and thence through holes 278 into the chamber 276 .between the heads 282 and 283 of valve 280. As the head 282 is larger than the head 283 the pressure from the fluid will tend to move the valve 280 to the left relatively to." the valve 269 with a force equal to the diflerence in the areas of the heads 282 and 283 of valve 280 multiplied by the pressure of'the fluid, and the spring 288 is constructed of such tension that the valve will be held against this force until the pressure of the fluid rises above the predetermined desired maximum when the spring will be compressed sufliciently to permit fluid to pass from the manifold 76 When the pressure is sufficiently relieved the spring 288 will return the valve' to its normal position. When the manifold 77 is the high pressure side of the circuit the fluid passes into the port between the heads 281 and 282 and as the head 281 is larger than the head 282 the pressure of the fluid tends to move the valve to the left against the tension of the spring 288 as before and should the pres- .sure be sufliciently high to overcome the tension of the spring the valve will be shifted and fluid allowed topass from the manifold 77 to the manifold 76, until the pressure in the manifold 77 falls below the desired maximum. When it is desired to permit the pump and motor to run independently of each other or'to permit either to remain stationary While the other is revolving, the valve 269 is moved to the left by means of the operating connections attached" to its stem 294 to permit the fluid from either manifold to'pass into the other. When the valve 269 is operated as described, the valve 280 being wholly supported by the valve 269 moves with it and hence the relative positions of the valves are not disturbed.

As the pressure in the main circuits sometimes fluctuates rapidly, there is at such times a tendency for the fluid in the passage 128 to surge back and forth with the result that the check valves 118 and 122 would, unless prevented, hammer on their seats and tend thereby not only to hammerthemselves to pieces but also make an objectionable noise. To overcome this I have pro- 1 vided these valves with the small cylindri-' cal stems 118 and 125 respectively working in the reduced bores as described. The valve stems are fitted into their bores so as to have a dashpot effect and thereby prevent too rapid reciprocation of the valves.

The operations of the several parts of the mechanismhave been fully described in connection with the description of their construction and I will now briefly describe the operation of the mechanism as a whole. Assuming the parts to be in the positions shown in'the drawings and the shaft '17 to be driven by some external source of power in a clockwise direction when viewed from the left hand end of Fig. 2 or as shown in Fig. 6, the pump pistons deliver fluid under pressure to the outer manifold 77 through their valve chambers. the valve crank pin, in the adjustment of the mechanism shown being 90 degrees behind the crank arm of the pump pistons in this direction of rotation. The fluid pressure from the manifold 77 operates the pistons in the motor cylinders to rotate the motor shaft in a counter clockwise direction, due to the selected arrangement of the motor crank 248 and the motor valve crank pin- 258 at its maximum speed.

Should it be desired to reduce the speed. the free end of the control lever 161 is moved to the right a distance corresponding to the change in speed desired, as shown in Fig. 7 or toward the machine and therebV-v through the rod 160 and floating lever The high pressure being in the outer manitold 77 the fluid therefrom passes into the port 112 and. passage 116 and thence through the check valve 118 into the passages 128 and 129 between the head132 of the valve 131 and the end of the passage 129. The pressure of, the fluid forces the valve to the left as shown in Fig. 8 uncovering the port 130 leading to the port 107. The port 107 having been connected to the port 106 as described, the fluid passes into the port 106 and thence through the ports and passages in the casings 70 and 71 to the front ends of the adjusting cylinders, thereby moving the pistons 66 and the attached yoke 63 to the right. The movement of the yoke causes the sleeve 54 to turn on the shaft 17 in a clockwise direction by reason of the threads and nut 56, 57, and, through the gears 53, 52 causes the eccentric bushing 19 to turn on the crank 18 thereby shortening the'crank arm of the pump pistons and reducing the quantity of fluid delivered to the motor and' consequently the speed of the motor. Should it be desired to reverse the direction of rotation of the motor the control lever 161 is moved toward the machine to a position sufficiently beyond its position which corresponds with the zero or no stroke position of the pump, to give the desired reverse speed. When the lever is so moved the yoke is moved as before by the pressure of the fluid in the main circuit until the pump reaches its zero position, but at this point there ceases to be, for obvious reasons, any working pressure in the 'main circuits and therefore the movement of the yoke momentarily ceases. When however the valve 94 has been moved far enough for the head 98 to cut oif'communication between the passages 187 and 188 of the normal leakage pump circuit, the pressure from the leakage pump rises in the passage 196 and the passage 129 between the heads of the valve 131 which portion of the passage 129 is, when there is no pressure against the head 132 of the valve 131. in communication with the bore 130 leading to the port 106. The port 106, by the movement of the valve 94 has been connected to the port 107 leading to the adjusting cylinders so that when the pressure rises sufficiently the adjusting yoke is shifted and the rotation of the eccentric bushingcontinued. Now, how

ever, the strokeof the pump pistons 'is increasing instead of decreasingythereby increasing the amount of fluid delivered to the motor and consequently accelerating the speed of the motor, but as the eccentric bushing rotates at twice the angular velocity of the valve crank pin 32, the relative positions of the real crank arm of the pump pistons and the crank arm of the valve crank pin are reversed and consequently the inner manifold 76 now becomes the high pressure side of the circuit and as the relative posi tion of the motor crank and the motor valve crank pin remains fixed, the direction of rotation of the motor is reversed. When it is desired to reduce the speed of reverse rotation or again drive the motor in the first described direction the control lever is moved in the opposite direction or away from the machine. The yoke 63 will then be shifted in the opposite direction by fluid pressure from the manifold 76 which enters the high pressure passage of the valve block through the port 115 and check valve 122 and passes through the port 105 to the rear ends of the adjusting cylinders, the fluid from the other side of the pistons 66 returning to the manifold 77 through the ports 107,108, passage 246 and check valve 144, the leakage pump supplying the fluid pressure as before to shift the adjusting mechanism from one side to the other of its zero position.

As stated above, my present invention is an improvement on the transmission mechanisms constituting the subject matter of my prior patent and application referred to and as such it embodies improvements in various parts of the mechanism and a reorganization of the transmission whereby such improved mechanisms may properly coiiperate to obtain a maximum efliciency of operation of the mechanism as a whole. Notable among the improvements presented in this application may be mentioned the formation of the adjusting cylinders in the pump casing between the pump cylinders whereby greater compactness is obtained and the use of pipe connections between the adjusting valve mechanism and the cylinders is avoided. The arrangement of the adjusting valves in a single valve block also constitutes a distinct improvement. By this arrangement numerous'pipe connections, which are more or less subject to leakage are dispensed with, the single packing between the valve block and its casing being easily made fluid tight Furthermore, the entire valve mechanism is readily removable for inspection or repairs or a new valve block may be substituted in a few moments without special fitting or adjustment.- The forged steel cylinders and valve chambers are also a distinct improvement and my improved copper packing permits their use with the integrally cast connecting manifolds.

While the above mentioned and other novel features disclosed all cooperate, as stated, in the attainment of a unitary result, many of such features have other useful applications andI have therefore claimed the same both per 86 and in combination with the cooperating parts of the transmission.

The V-shaped notches in the edges of the active heads of the pump valves which are shown in the drawings of this case are not 

